JP6306458B2 - Constant velocity joint support bearing and constant velocity joint outer ring - Google Patents

Constant velocity joint support bearing and constant velocity joint outer ring Download PDF

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JP6306458B2
JP6306458B2 JP2014144680A JP2014144680A JP6306458B2 JP 6306458 B2 JP6306458 B2 JP 6306458B2 JP 2014144680 A JP2014144680 A JP 2014144680A JP 2014144680 A JP2014144680 A JP 2014144680A JP 6306458 B2 JP6306458 B2 JP 6306458B2
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constant velocity
velocity joint
outer ring
support bearing
bearing
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JP2016020717A (en
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真 友上
真 友上
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NTN Corp
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NTN Corp
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Priority to JP2014144680A priority Critical patent/JP6306458B2/en
Priority to CN201580038088.9A priority patent/CN106536950B/en
Priority to EP15822425.3A priority patent/EP3171046A4/en
Priority to PCT/JP2015/069897 priority patent/WO2016009960A1/en
Priority to US15/324,056 priority patent/US20170204898A1/en
Publication of JP2016020717A publication Critical patent/JP2016020717A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C11/00—Pivots; Pivotal connections
    • F16C11/04—Pivotal connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/22—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or type of main drive shafting, e.g. cardan shaft
    • B60K17/24—Arrangements of mountings for shafting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/38—Ball cages
    • F16C33/44—Selection of substances
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/581—Raceways; Race rings integral with other parts, e.g. with housings or machine elements such as shafts or gear wheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/64—Special methods of manufacture
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C43/00—Assembling bearings
    • F16C43/04—Assembling rolling-contact bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/06—Drive shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/41—Couplings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/38—Ball cages
    • F16C33/41—Ball cages comb-shaped
    • F16C33/412—Massive or moulded comb cages, e.g. snap ball cages
    • F16C33/414—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages
    • F16C33/416—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages made from plastic, e.g. injection moulded comb cages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
    • F16C33/782—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region
    • F16C33/7826—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region of the opposing surface cooperating with the seal, e.g. a shoulder surface of a bearing ring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D2003/22326—Attachments to the outer joint member, i.e. attachments to the exterior of the outer joint member or to the shaft of the outer joint member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D3/226—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a cylinder co-axial with the respective coupling part
    • F16D3/227—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a cylinder co-axial with the respective coupling part the joints being telescopic

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Manufacturing & Machinery (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Rolling Contact Bearings (AREA)
  • Sealing Of Bearings (AREA)

Description

この発明は、等速ジョイントのサポート軸受に関するものである。   The present invention relates to a support bearing for a constant velocity joint.

自動車において、エンジンの駆動力を各車輪へと伝達する駆動軸は、その伝達部位により、プロペラシャフトとドライブシャフトに大別される。自動車は、その駆動方式により、フロントエンジン・前輪駆動車（ＦＦ車）、フロントエンジン・後輪駆動車（ＦＲ車）、四輪駆動車（４ＷＤ車）、リアエンジン・後輪駆動車（ＲＲ車）などに分別されている。   In an automobile, a drive shaft that transmits the driving force of an engine to each wheel is roughly classified into a propeller shaft and a drive shaft according to the transmission part. Cars are driven by front engine / front-wheel drive vehicles (FF vehicles), front engines / rear-wheel drive vehicles (FR vehicles), four-wheel drive vehicles (4WD vehicles), rear engines / rear-wheel drive vehicles (RR vehicles). ) And so on.

車の高性能化と乗り心地向上の流れにより、多くのＦＦ車は、直進時の左右のドライブシャフトの角度がほぼ等しくなるシャフト等長設計が採用されている。   Due to the trend toward higher vehicle performance and improved ride comfort, many FF vehicles adopt a shaft isometric design in which the left and right drive shaft angles are almost equal when traveling straight.

図７はＦＦ車の前輪のトルク伝達部分の概略図を示している。図７のように、図示しない原動機からの動力は、デファレンシャル装置１０１で左右に分配される。分配後の一方の動力は等速ジョイント１１０、シャフト１２１、等速ジョイント１２２を主な構成部品とするドライブシャフト１を介してホイール軸受１２３および車輪に伝達され、他方の動力は、等速ジョイント１１０ａ、シャフト１２１ａ、等速ジョイント１２２ａを主な構成部品とするドライブシャフト１aを介してホイール軸受１２３ａおよび車輪に伝達される。等速ジョイント１１０、１１０ａは、軸方向変位および角度変位を許容する摺動式等速ジョイントであり、等速ジョイント１２２、１２２ａは、軸方向変位は許容しないが大きな角度変位（作動角４７度程度）を許容する固定式等速ジョイントである。   FIG. 7 shows a schematic diagram of the torque transmission portion of the front wheel of the FF vehicle. As shown in FIG. 7, power from a prime mover (not shown) is distributed to the left and right by the differential device 101. One power after distribution is transmitted to the wheel bearing 123 and the wheel via the drive shaft 1 whose main components are the constant velocity joint 110, the shaft 121, and the constant velocity joint 122, and the other power is transmitted to the constant velocity joint 110a. The shaft 121a and the constant velocity joint 122a are transmitted to the wheel bearing 123a and the wheel via the drive shaft 1a having main components. The constant velocity joints 110 and 110a are slidable constant velocity joints that allow axial displacement and angular displacement, and the constant velocity joints 122 and 122a do not allow axial displacement but have a large angular displacement (operating angle of about 47 degrees). ) Is a fixed type constant velocity joint.

エンジンが横置きタイプの場合、デファレンシャル装置１０１は車両の中央より片寄った位置になる。シャフト等長設計の場合、片寄った位置に設置されたデファレンシャル装置１０１に結合するドライブシャフト１、（１ａ）のインボード側の等速ジョイント１１０（１１０ａ）の外輪の軸部は、一方が短軸、もう一方が長軸の組合せを使用する設計が多い。   When the engine is a horizontal type, the differential device 101 is offset from the center of the vehicle. In the case of the shaft equal length design, one of the shaft portions of the outer ring of the constant velocity joint 110 (110a) on the inboard side of the drive shaft 1 (1a) coupled to the differential device 101 installed at an offset position is a short axis. In many cases, the other uses a combination of long axes.

図８はインボード側の等速ジョイントを示す説明図、図９はサポート軸受部を示す拡大図である。図７〜図９に示すように、インボード側の等速ジョイント１１０は、カップ１１１と軸部１１２が一体構造となっている。そして、インボード側の等速ジョイント１１０における長軸側の軸部１１２は、デファレンシャル装置１０１との嵌合部だけでは支持が不安定になるので、軸部１１２に軸受１３０を取り付け、その軸受１３０がブラケット１４０を介してエンジン又はトランスミッションケースに固定されている。この軸受１３０は、サポート軸受と呼ばれている。   FIG. 8 is an explanatory view showing a constant velocity joint on the inboard side, and FIG. 9 is an enlarged view showing a support bearing portion. As shown in FIGS. 7 to 9, the constant velocity joint 110 on the inboard side has a cup 111 and a shaft portion 112 that are integrated. Since the long shaft side shaft portion 112 of the inboard constant velocity joint 110 is unstable only by the fitting portion with the differential device 101, a bearing 130 is attached to the shaft portion 112, and the bearing 130 is attached. Is fixed to the engine or transmission case via a bracket 140. This bearing 130 is called a support bearing.

軸部１１２の材質は、例えば、Ｓ４５Ｃ〜Ｓ５５Ｃの中炭素鋼で、強度を確保するために、軸部１１２の表面に高周波熱処理を施して硬化している。この軸部１１２にサポート軸受１３０が取り付けられている。サポート軸受１３０は、内輪１３１、外輪１３２、転動体としてのボール１３３、保持器１３４、シール１３５で構成されている。サポート軸受１３０はインボード側の等速ジョイントの外輪のカップ１１１に近い軸部１１２に嵌合し、止め輪１３６で軸方向に固定されている。 The material of the shaft portion 112 is, for example, medium carbon steel of S45C to S55C, and the surface of the shaft portion 112 is hardened by performing high-frequency heat treatment in order to ensure strength. A support bearing 130 is attached to the shaft portion 112. The support bearing 130 includes an inner ring 131, an outer ring 132, balls 133 as rolling elements, a cage 134, and a seal 135. The support bearing 130 is fitted to the shaft portion 112 near the cup 111 of the outer ring of the constant velocity joint on the inboard side, and is fixed in the axial direction by a retaining ring 136.

燃費向上のためには、軸受部材にも軽量化が望まれており、サポート軸受１３０を小型化することが考えられる。   In order to improve fuel consumption, weight reduction is also desired for the bearing member, and it is conceivable to reduce the size of the support bearing 130.

ところで、従来のサポート軸受１３０は、インボード側の等速ジョイントの外輪のカップ１１１に近い軸部１１２に嵌合し、止め輪１３６で軸方向に固定されている。 Incidentally, the conventional support bearing 130 is fitted to the shaft portion 112 near the cup 111 of the outer ring of the constant velocity joint on the inboard side, and is fixed in the axial direction by the retaining ring 136.

サポート軸受１３０は、インボード側の等速ジョイントの外輪の軸部１１２の小端面側から組付けるため、サポート軸受１３０の内径は、軸部１１２の最大径部、すなわち、図８のＡの径より大きくなければならない。軸部１１２の最大径は、車両のデファレンシャル装置１０１への取り付け部形状で決まる寸法で、ドライブシャフト側の都合で小さくすることは困難である。   Since the support bearing 130 is assembled from the small end face side of the shaft portion 112 of the outer ring of the constant velocity joint on the inboard side, the inner diameter of the support bearing 130 is the maximum diameter portion of the shaft portion 112, that is, the diameter of A in FIG. Must be bigger. The maximum diameter of the shaft portion 112 is a dimension determined by the shape of the attachment portion to the differential device 101 of the vehicle, and it is difficult to reduce it for convenience on the drive shaft side.

すなわち、図８に示すように、デファレンシャル装置１０１の構造で、軸部１１２の先端は、サイドギア嵌合部１１３、デフリングギアとの滑り軸受部１１４、デフオイルシール接触部１１５、オイルシール保護のためのダストカバー装着部１１５ａからサポート軸受１３０と嵌合する軸になる。これらの軸では、サイドギア嵌合部１１３、デフリングギアとの滑り軸受部１１４、デフオイルシール接触部１１５、ダストカバー装着部１１５ａの順で径が大きくなる。   That is, as shown in FIG. 8, in the structure of the differential device 101, the tip of the shaft portion 112 has a side gear fitting portion 113, a sliding bearing portion 114 with a diff ring gear, a differential oil seal contact portion 115, and an oil seal protection. It becomes an axis | shaft which fits with the support bearing 130 from the dust cover mounting part 115a. In these shafts, the diameter increases in the order of the side gear fitting portion 113, the sliding bearing portion 114 with the differential ring gear, the differential oil seal contact portion 115, and the dust cover mounting portion 115a.

言い換えれば、軸部１１２の最大径部は、デファレンシャル装置１０１のシール径により決まり、ドライブシャフト側の都合で小さくすることができない。サポート軸受１３０は、等速ジョイントを支えてスムーズに回転させることが機能であり、この軸受１３０に負荷される荷重は小さい。よって、小型の軸受が設計可能であるが、軸への組付の関係で軸受の内径を軸部最大径より小さくすることができない。   In other words, the maximum diameter portion of the shaft portion 112 is determined by the seal diameter of the differential device 101 and cannot be reduced for convenience on the drive shaft side. The support bearing 130 functions to support the constant velocity joint and rotate smoothly, and the load applied to the bearing 130 is small. Therefore, although a small bearing can be designed, the inner diameter of the bearing cannot be made smaller than the maximum diameter of the shaft portion because of the assembly to the shaft.

また、車両の床下部位でドライブシャフトを支持するサポート軸受は、水や泥水が飛散する環境で使用されるため、これらの水や泥水が内輪と外輪との間の軸受空間への浸入を防止するシール装置が用いられている。シール装置を用いたサポート軸受が種々提案されている。例えば、特許文献１に記載のものは、高いシール性能と低トルクロスを実現したサポート軸受が提案されている。この特許文献１は、デファレンシャル装置と等速ジョイントとの間でトルクを伝達する中間シャフトに固定される内輪、ブラケットを介して自動車の車体に固定される外輪、および内・外輪の軌道面間に介在させた転動体を有するサポート軸受をシールする装置であって、前記中間シャフトにブラケットの近傍まで延びるカバー部材を固定し、ブラケットとカバー部材の何れか一方に、他方に対して摺動可能なブラシを設けている。   In addition, support bearings that support the drive shaft under the floor of the vehicle are used in an environment where water or muddy water scatters. Therefore, these water and muddy water prevent intrusion into the bearing space between the inner ring and the outer ring. A sealing device is used. Various support bearings using a sealing device have been proposed. For example, the support bearing which implement | achieved the high sealing performance and the low torque cross is proposed for the thing of patent document 1. FIG. This patent document 1 describes an inner ring fixed to an intermediate shaft that transmits torque between a differential device and a constant velocity joint, an outer ring fixed to a vehicle body via a bracket, and a raceway surface between the inner and outer rings. A device for sealing a support bearing having an intervening rolling element, wherein a cover member extending to the vicinity of the bracket is fixed to the intermediate shaft, and one of the bracket and the cover member is slidable with respect to the other A brush is provided.

また、特許文献２には、水や泥水による外輪の外径面での錆の発生を長期間に亘って防止するサポート軸受が提案されている。この特許文献２は、内輪と外輪の間の軸受空間を接触シールで密封し、内輪回転で使用される密封型転がり軸受において、前記外輪の外径面をゴムまたは樹脂の皮膜で覆っている。   Patent Document 2 proposes a support bearing that prevents rust generation on the outer diameter surface of the outer ring due to water or muddy water over a long period of time. In Patent Document 2, a bearing space between an inner ring and an outer ring is sealed with a contact seal, and an outer diameter surface of the outer ring is covered with a rubber or resin film in a sealed type rolling bearing used for inner ring rotation.

特開２０１２−３６９７３号公報JP 2012-36973 A 特開２００７−１２７１５７号公報JP 2007-127157 A

上記した特許文献１、２に示すように、従来は、軸受の寿命や、シール性や錆の発生などの対策については種々提案されている。しかしながら、燃費向上のためには、軸受部材にも軽量化が望まれているが、上記した特許文献１、２には、軸受部材の軽量化については考慮されていない。   As shown in Patent Documents 1 and 2 described above, conventionally, various measures have been proposed for measures such as bearing life, sealability, and generation of rust. However, in order to improve fuel efficiency, the bearing member is also required to be reduced in weight, but the above Patent Documents 1 and 2 do not consider the reduction in weight of the bearing member.

上述したように、サポート軸受は、軸部への組付の関係で軸受の内径を軸部の最大径より小さくすることができない。このため、サポート軸受の小型化にも限界があった。   As described above, in the support bearing, the inner diameter of the bearing cannot be made smaller than the maximum diameter of the shaft portion because of the assembly to the shaft portion. For this reason, there was a limit to downsizing the support bearing.

そこで、この発明は、等速ジョイントのサポート軸受において、小型化を図り、軽量化を図ることを課題とするものである。   Accordingly, an object of the present invention is to reduce the size and weight of a support bearing for a constant velocity joint.

前記の課題を解決するために、この発明は、インボード側の等速ジョイントの外輪の軸部に、軸受の転走面が形成され、この転走面の溝底の径がインボード側の等速ジョイントの外輪の軸部の最大径より小さく、この転走面と対向するように、サポート軸受用外輪が配置され、前記転走面とサポート軸受用外輪の転走面との間に、保持器で保持された複数の転動体が配置されていることを特徴とする。 In order to solve the above-described problems, the present invention is configured such that a rolling surface of a bearing is formed on a shaft portion of an outer ring of a constant velocity joint on an inboard side, and the diameter of the groove bottom of the rolling surface is the inboard side An outer ring for support bearings is disposed so as to be smaller than the maximum diameter of the shaft portion of the outer ring of the constant velocity joint and facing the rolling surface, and between the rolling surface and the rolling surface of the outer ring for support bearing. A plurality of rolling elements held by a cage are arranged.

また、前記転走面を挟むようにシール接触面を設け、前記転走面とシール接触面を高周波焼き入れにより硬化させることが好ましい。 Furthermore, the provided sealing contact surface so as to sandwich the rolling surface, is to be preferably hardened by prior induction hardening the Kiten contact surface and the seal contact surface.

また、前記シール接触面の外径がインボード側の等速ジョイントの外輪の軸部の最大径より大きいことが望ましい。   The outer diameter of the seal contact surface is preferably larger than the maximum diameter of the shaft portion of the outer ring of the constant velocity joint on the inboard side.

なお、ここではドライブシャフトを車両に装着した状態で車両の中央よりをインボード側といい、車両の外側よりをアウトボード側という。   Here, the center of the vehicle with the drive shaft mounted on the vehicle is referred to as the inboard side, and the outside of the vehicle is referred to as the outboard side.

また、前記保持器としては、樹脂製保持器を用いることができる。   Moreover, a resin-made cage can be used as the cage.

また、この発明では、インボード側の等速ジョイントの外輪であって、外輪はカップと軸部が一体構造になっており、前記カップの内面にはトルク伝達部材が転動する複数の直線状のトラック溝が形成され、軸部の外径面にサポート軸受の転走面が形成され、この転走面の溝底の径がインボード側の等速ジョイントの外輪の軸部の最大径より小さいことを特徴とする。 Further, according to the present invention, the outer ring of the constant velocity joint on the inboard side, the outer ring has an integral structure of the cup and the shaft portion, and a plurality of linear shapes on which the torque transmission member rolls on the inner surface of the cup Track groove is formed, the rolling surface of the support bearing is formed on the outer diameter surface of the shaft portion, and the diameter of the groove bottom of this rolling surface is larger than the maximum diameter of the shaft portion of the outer ring of the constant velocity joint on the inboard side It is small .

以上のように、この発明によれば、インボード側の等速ジョイントの外輪の軸部の最大径をサポート軸受の内輪外径寸法にすることができ、従来の別体のサポート軸受より、小型設計が可能となる。さらに、軸受の内輪を省略することができ、部品点数が少なくなり、更に軽量化が図れる。   As described above, according to the present invention, the maximum diameter of the shaft portion of the outer ring of the constant velocity joint on the inboard side can be made the inner ring outer diameter size of the support bearing, which is smaller than the conventional separate support bearing. Design becomes possible. Furthermore, the inner ring of the bearing can be omitted, the number of parts is reduced, and further weight reduction can be achieved.

この発明の実施形態にかかるインボード側の等速ジョイントを示す説明図である。It is explanatory drawing which shows the constant velocity joint by the side of the inboard concerning embodiment of this invention. この発明の実施形態にかかるサポート軸受部を示す拡大図である。It is an enlarged view which shows the support bearing part concerning embodiment of this invention. この発明の実施形態にかかるサポート軸受部の等速ジョイントの軸部を示す拡大図である。It is an enlarged view which shows the axial part of the constant velocity joint of the support bearing part concerning embodiment of this invention. この発明の実施形態にかかるインボード側の等速ジョイントにサポート軸受を組み付ける状態を示す斜視図である。It is a perspective view which shows the state which attaches a support bearing to the constant velocity joint by the side of the inboard concerning this Embodiment. この発明の実施形態にかかるインボード側の等速ジョイントにサポート軸受を組み付ける状態を示す斜視図である。It is a perspective view which shows the state which attaches a support bearing to the constant velocity joint by the side of the inboard concerning this Embodiment. この発明をドライブシャフトに用いた実施形態を示す説明図である。It is explanatory drawing which shows embodiment using this invention for the drive shaft. ＦＦ車の前輪のトルク伝達部分の概略図を示している。The schematic of the torque transmission part of the front wheel of FF vehicle is shown. 従来のインボード側の等速ジョイントを示す説明図である。It is explanatory drawing which shows the conventional constant velocity joint by the side of an inboard. 図８に示す等速ジョイントのサポート軸受部を示す拡大図である。It is an enlarged view which shows the support bearing part of the constant velocity joint shown in FIG.

以下、この発明の実施の形態を添付図面に基づいて説明する。この発明は、自動車に使用するドライブシャフトのインボード側の等速ジョイントをエンジンまたはトランスミッションケースに固定し、且つ、ドライブシャフトの回転をスムーズに行うサポート軸受に関するものである。   Embodiments of the present invention will be described below with reference to the accompanying drawings. The present invention relates to a support bearing that fixes a constant velocity joint on an inboard side of a drive shaft used in an automobile to an engine or a transmission case and smoothly rotates the drive shaft.

従来より、図１および図２に示すように、インボード側の等速ジョイント３の外輪の軸部３２は強度を確保するために、Ｓ４５Ｃ〜Ｓ５５Ｃ程度の中炭素鋼に高周波焼入れを行っている。表面はＨＲＣ（ロックウエル硬度のＣスケール）で５８〜６４程度の硬度を得ることができる。この硬度であれば、軽負荷荷重の軸受の転動面して利用することは可能である。そこで、この発明は、サポート軸受４は従来の別体の内輪の代わりに、インボード側の等速ジョイント３の外輪の軸部３２に、ボール転走面３３を成形してサポート軸受４の内輪をインボード側の等速ジョイント３の外輪の軸部３２と一体化したものである。   Conventionally, as shown in FIGS. 1 and 2, the shaft portion 32 of the outer ring of the constant velocity joint 3 on the inboard side has been induction-hardened to medium carbon steel of about S45C to S55C. . The surface can have a hardness of about 58 to 64 by HRC (C scale of Rockwell hardness). With this hardness, it can be used as a rolling surface of a light load bearing. Therefore, in the present invention, the support bearing 4 is formed by forming the ball rolling surface 33 on the shaft portion 32 of the outer ring of the constant velocity joint 3 on the inboard side in place of the conventional separate inner ring, thereby forming the inner ring of the support bearing 4. Is integrated with the shaft portion 32 of the outer ring of the constant velocity joint 3 on the inboard side.

この構造を取ることにより、軸部３２の外径面に形成された転走面３３の溝底の径がインボード側の等速ジョイント３の外輪の軸部３２の最大径Ａ（ダストカバー装着部３２５ａ）より小さくすることができ、従来の別体のサポート軸受より、小型設計が可能である。さらに、軸受の内輪を省略することができ、部品点数が少なくなり、更に軽量化が図れる。   By adopting this structure, the diameter of the groove bottom of the rolling surface 33 formed on the outer diameter surface of the shaft portion 32 is the maximum diameter A of the outer ring shaft portion 32 of the constant velocity joint 3 on the inboard side (attaching the dust cover). Part 325a) and can be made smaller than conventional separate support bearings. Furthermore, the inner ring of the bearing can be omitted, the number of parts is reduced, and further weight reduction can be achieved.

この場合、サポート軸受４のボールピッチ径が小さくなるので、別体軸受と等価の負荷容量にはできないが、サポート軸受４はインボード側の等速ジョイント３を支えることが目的であり、必要負荷容量は小さく、負荷容量が低下しても使用可能である。   In this case, since the ball pitch diameter of the support bearing 4 is reduced, the load capacity cannot be equivalent to that of a separate bearing, but the support bearing 4 is intended to support the constant velocity joint 3 on the inboard side, and the necessary load The capacity is small, and it can be used even when the load capacity decreases.

図１〜図３に従いこの発明の実施形態を詳述する。この実施形態のサポート軸受４は、インボード側の等速ジョイント３の外輪のカップ３１に近い軸部に設けられている。インボード側の等速ジョイント３は、カップ３１と軸部３２が一体構造となっている。そして、インボード側の等速ジョイント３の軸部３２の先端部は、デファレンシャル装置１０１と嵌合する。   The embodiment of the present invention will be described in detail with reference to FIGS. The support bearing 4 of this embodiment is provided on a shaft portion near the cup 31 of the outer ring of the constant velocity joint 3 on the inboard side. In the constant velocity joint 3 on the inboard side, the cup 31 and the shaft portion 32 have an integral structure. Then, the distal end portion of the shaft portion 32 of the constant velocity joint 3 on the inboard side is fitted to the differential device 101.

軸部３２の先端は、先端部からサイドギア嵌合部３２３、デフリングギアとの滑り軸受部３２４、デフオイルシール接触部３２５、オイルシール保護のためのダストカバー装着部３２５ａで構成されている。デファレンシャル装置１０１の内の軸では、前述したように、サイドギア嵌合部３２３、デフリングギアとの滑り軸受部３２４、デフオイルシール接触部３２５、ダストカバー装着部３２５ａの順で径が大きくなる。ダストカバー装着部３２５ａの径が最大径Ａとなる。   The distal end of the shaft portion 32 includes a side gear fitting portion 323, a sliding bearing portion 324 with a differential ring gear, a differential oil seal contact portion 325, and a dust cover mounting portion 325a for protecting the oil seal. As described above, the diameter of the shaft in the differential device 101 increases in the order of the side gear fitting portion 323, the sliding bearing portion 324 with the differential ring gear, the differential oil seal contact portion 325, and the dust cover mounting portion 325a. The diameter of the dust cover mounting portion 325a is the maximum diameter A.

この発明では、従来のサポート軸受１３０の内輪１３１の代わりに、インボード側の等速ジョイント３の外輪の軸部３２の外径面に、ボール転走面３３を直接形成し、サポート軸受４の内輪をインボード側の等速ジョイントの外輪の軸部３２と一体化したものである。すなわち、この実施形態では、従来、サポート軸受４を装着する部分に、サポート軸受４のボール転走面３３とその両側にシール接触面３４が形成されている。軸部３２の外径面に形成された転走面３３の溝底の径はインボード側の等速ジョイント３の外輪の軸部３２の最大径Ａ（ダストカバー装着部３２５ａ）より小さくすることができる。この結果、従来よりも小径のサポート軸受４を達成することができ、車両への軽量化が可能となる。   In the present invention, instead of the inner ring 131 of the conventional support bearing 130, the ball rolling surface 33 is formed directly on the outer diameter surface of the shaft portion 32 of the outer ring of the constant velocity joint 3 on the inboard side. The inner ring is integrated with the shaft portion 32 of the outer ring of the constant velocity joint on the inboard side. That is, in this embodiment, conventionally, a ball rolling surface 33 of the support bearing 4 and seal contact surfaces 34 are formed on both sides of the portion where the support bearing 4 is mounted. The diameter of the groove bottom of the rolling surface 33 formed on the outer diameter surface of the shaft portion 32 should be smaller than the maximum diameter A (dust cover mounting portion 325a) of the shaft portion 32 of the outer ring of the constant velocity joint 3 on the inboard side. Can do. As a result, the support bearing 4 having a smaller diameter than that of the conventional one can be achieved, and the weight of the vehicle can be reduced.

軸部３２の材質は、上述したように、強度を確保するために、Ｓ４５Ｃ〜Ｓ５５Ｃの中炭素鋼が好ましく、軸部３２の表面は、ボール転走面３３とシール接触面３４も含め高周波熱処理を施して硬化している。   As described above, the material of the shaft portion 32 is preferably a medium carbon steel of S45C to S55C in order to ensure the strength, and the surface of the shaft portion 32 includes high-frequency heat treatment including the ball rolling surface 33 and the seal contact surface 34. Has been cured.

この軸部３２のボール転走面３３が設けられた箇所が、サポート軸受４の内輪の機能を果たし、このボール転走面３３を用いてサポート軸受４を構成する。このボール転走面３３と対向するように、サポート軸受用外輪４２が配置され、ボール転走面３３とサポート軸受用外輪４２の転走面４２ａとの間に、転動体としての複数のボール４３が配置される。さらに、この複数個のボール４３を円周方向等間隔に保持する保持器４４を設けるとともに、シール接触面３４とサポート軸受用外輪４２の軸方向両端開口部に軸受内部を密封する軸受シール４５がそれぞれ設けられる。密封された軸受内部の少なくともボール４３の周囲にグリースが封入されている。軸受シール４５は一端がサポート軸受用外輪４２に固定され、他端が軸部３２のシール接触面３４と接触する。   The portion of the shaft portion 32 provided with the ball rolling surface 33 functions as an inner ring of the support bearing 4, and the ball bearing surface 33 is used to configure the support bearing 4. A support bearing outer ring 42 is arranged to face the ball rolling surface 33, and a plurality of balls 43 as rolling elements are provided between the ball rolling surface 33 and the rolling surface 42 a of the support bearing outer ring 42. Is placed. Further, a cage 44 for holding the plurality of balls 43 at equal intervals in the circumferential direction is provided, and a bearing seal 45 for sealing the inside of the bearing at the seal contact surface 34 and the opening in the axial direction of the support bearing outer ring 42 is provided. Each is provided. Grease is sealed at least around the ball 43 inside the sealed bearing. One end of the bearing seal 45 is fixed to the support bearing outer ring 42, and the other end contacts the seal contact surface 34 of the shaft portion 32.

軸受シール４５は、ゴム成形体単独でもよく、或いはゴム成形体と金属板、プラスチック板、セラミック板との複合体であってもよい。   The bearing seal 45 may be a rubber molded body alone or a composite of a rubber molded body and a metal plate, a plastic plate, or a ceramic plate.

サポート軸受４のボール転走面３３をインボード側の等速ジョイントの外輪の軸部３２に設けることで、従来の軸受構造の内輪を省いた構造となる。サポート軸受用外輪４２、ボール４３、保持器４４、軸受シール４５の材料、加工方法などは、従来のものと同じでよい。   By providing the ball rolling surface 33 of the support bearing 4 on the shaft portion 32 of the outer ring of the constant velocity joint on the inboard side, the inner ring of the conventional bearing structure is omitted. The materials and processing methods of the support bearing outer ring 42, the ball 43, the cage 44, and the bearing seal 45 may be the same as the conventional one.

次に、この実施形態の外輪の軸部３２と一体に構成したサポート軸受４の組立手順を図４及び図５を参照して説明する。まず、図４（ａ）に示すように、サポート軸受４を装着する部分に、軸受のボール転走面３３とシール接触面３４を形成した軸部３２を有する等速ジョイントの外輪を用意する。図４（ｂ）に示すように、この軸部３２のサイドギア嵌合部３２３より、一方の軸受シール４５を奥まで挿入する。   Next, an assembling procedure of the support bearing 4 constructed integrally with the outer ring shaft portion 32 of this embodiment will be described with reference to FIGS. First, as shown in FIG. 4A, an outer ring of a constant velocity joint having a shaft portion 32 in which a ball rolling surface 33 and a seal contact surface 34 of the bearing are formed at a portion where the support bearing 4 is mounted is prepared. As shown in FIG. 4B, one bearing seal 45 is inserted from the side gear fitting portion 323 of the shaft portion 32 to the back.

続いて、図４（ｃ）に示すように、サポート軸受用外輪４２を挿入し、図５（ａ）に示すように、サポート軸受用外輪４２を偏芯させ、軸部３２のボール転走面３３とサポート軸受用外輪４２の転走面４２ａとの間に複数個のボール４３を挿入する。図５（ａ）は複数個のボール４３が挿入完了した後を示している。その後、図５（ｂ）に示すように、ボール４３を等配後、サイドギア嵌合部３２３より、保持器４４を組み込み、グリースを封入し、更に、他方の軸受シール４５を組み込んで、シール接触面３４とサポート軸受用外輪４２の軸方向両端開口部に軸受シール４５を装着して軸受内部を密封する。そして、図５（ｃ）に示すような、軸部３２に一体に形成されたサポート軸受４が得られる。
Subsequently, as shown in FIG. 4 (c), the support bearing outer ring 42 is inserted, and as shown in FIG. 5 (a), the support bearing outer ring 42 is eccentric, and the ball rolling surface of the shaft portion 32 is obtained. A plurality of balls 43 are inserted between 33 and the rolling surface 42 a of the support bearing outer ring 42. FIG. 5A shows a state after the plurality of balls 43 have been inserted. After that, as shown in FIG. 5B, after the balls 43 are arranged equally, the cage 44 is assembled from the side gear fitting portion 323, the grease is sealed, and the other bearing seal 45 is further incorporated to make a seal contact. Bearing seals 45 are attached to both ends in the axial direction of the surface 34 and the support bearing outer ring 42 to seal the inside of the bearing. Then, as shown in FIG. 5 (c), support bearing 4 formed integrally with the shaft portion 32 is obtained.

サポート軸受４は設計上、シール接触面３４の外径が軸部３２の最大径Ａ（図１参照）より大きいことが好ましいが、シールが問題なく、シール装着位置まで組み込めれば小さくてもよい。   The support bearing 4 is preferably designed so that the outer diameter of the seal contact surface 34 is larger than the maximum diameter A of the shaft portion 32 (see FIG. 1). .

軸受４の内側となるボール転走面３３は、軸受寿命の観点より表面硬度はＨＲＣ５８以上が望ましい。ボール転走面３３は、一般的に、研削加工後、仕上げ加工（スーパーフィニッシュ）を施すが、サポート軸受４は負荷が軽く、最高回転数も低いため、仕上げ加工（スーパーフィニッシュ）を省略してもよい。なお、この実施形態では、保持器４４は、冠型の樹脂製保持器を用いることてドライブシャフトに組み立てが可能となっている。   The ball rolling surface 33 that is the inner side of the bearing 4 is preferably HRC58 or more in surface hardness from the viewpoint of bearing life. The ball rolling surface 33 is generally subjected to a finishing process (super finish) after grinding, but the support bearing 4 is light in load and has a low maximum rotational speed, so the finishing process (super finish) is omitted. Also good. In this embodiment, the retainer 44 can be assembled to the drive shaft by using a crown-shaped resin retainer.

図６は、この発明のサポート軸受をドライブシャフトに用いた実施形態を示す説明図である。ドライブシャフト１のデファレンシャル装置側に、この発明の実施形態の摺動式等速ジョイントである等速ジョイント３が設けられ、他方に固定式等速ジョイントである等速ジョイント５が設けられている。   FIG. 6 is an explanatory view showing an embodiment in which the support bearing of the present invention is used for a drive shaft. A constant velocity joint 3 that is a sliding type constant velocity joint according to the embodiment of the present invention is provided on the differential device side of the drive shaft 1, and a constant velocity joint 5 that is a fixed type constant velocity joint is provided on the other side.

この等速ジョイント３は、外輪のカップ３１と軸部３２が一体構造となっている。この軸部３２の先端は、先端部からサイドギア嵌合部３２３、デフリングギアとの滑り軸受部３２４、デフオイルシール接触部３２５、オイルシール保護のためのダストカバー装着部３２５ａが設けられている。   In this constant velocity joint 3, an outer ring cup 31 and a shaft portion 32 have an integral structure. The tip of the shaft portion 32 is provided with a side gear fitting portion 323, a sliding bearing portion 324 with a differential ring gear, a differential oil seal contact portion 325, and a dust cover mounting portion 325a for protecting the oil seal.

この軸部３２の外径面に、軸受４のボール転走面３３とその両側にシール接触面３４が形成されている。このボール転走面３３と対向するように、サポート軸受用外輪４２が配置され、ボール転走面３３とサポート軸受用外輪４２の転走面４２ａとの間に、保持器に保持された複数のボール４３が配置される（図２参照）。サポート軸受４の内輪をインボード側の等速ジョイントの外輪の軸部３２と一体化して設けている。このサポート軸受４がブラケットを介してエンジン又はトランスミッションケースに固定される。   A ball rolling surface 33 of the bearing 4 and seal contact surfaces 34 are formed on both sides of the outer diameter surface of the shaft portion 32. A support bearing outer ring 42 is disposed so as to face the ball rolling surface 33, and a plurality of holding rollers are held between the ball rolling surface 33 and the rolling surface 42 a of the support bearing outer ring 42. A ball 43 is arranged (see FIG. 2). The inner ring of the support bearing 4 is provided integrally with the shaft part 32 of the outer ring of the constant velocity joint on the inboard side. The support bearing 4 is fixed to the engine or transmission case via a bracket.

等速ジョイント３の内輪側にシャフト１２１が連結されている。外輪のカップ３１の内面および内輪３１３の外面に軸方向の複数の直線状トラック溝３１４、３１５を形成している。トラック溝３１４、３１５間に組み込んだボール３１６をケージ３１７で支持し、このケージ３１７の外周を球面とし、かつ内周を内輪３１３の外周に適合する球面としている。   A shaft 121 is connected to the inner ring side of the constant velocity joint 3. A plurality of linear track grooves 314 and 315 in the axial direction are formed on the inner surface of the outer ring cup 31 and the outer surface of the inner ring 313. A ball 316 incorporated between the track grooves 314 and 315 is supported by a cage 317, the outer periphery of the cage 317 is a spherical surface, and the inner periphery is a spherical surface that fits the outer periphery of the inner ring 313.

外輪のカップ３１から、内輪３１３に連結されたシャフト１２１にかけて、ゴム組成物や樹脂の成形体であるブーツ３１９が装着されている。   A boot 319, which is a molded article of a rubber composition or a resin, is mounted from the cup 31 of the outer ring to the shaft 121 connected to the inner ring 313.

ブーツ３１９は、外輪のカップ３１に嵌合されて固定される外筒端部（大径取付部）３１９ａと、内輪に連結されたシャフト１２１に嵌合されて固定される内筒端部（小径取付部）３１９ｂと、これら外筒端部３１９ａと内筒端部３１９ｂとの間を繋ぐ複数の山谷を有する蛇腹状の屈曲部３１９ｃとを備え、等速ジョイントを密封するように覆うものである。   The boot 319 includes an outer cylinder end portion (large-diameter mounting portion) 319a which is fitted and fixed to the cup 31 of the outer ring, and an inner cylinder end portion (small diameter) which is fitted and fixed to the shaft 121 connected to the inner ring. (Attachment part) 319b and a bellows-like bent part 319c having a plurality of peaks and valleys connecting between the outer cylinder end part 319a and the inner cylinder end part 319b, and covers the constant velocity joint so as to be sealed. .

この密封空間に、グリースなどの潤滑剤（図示省略）が封入されている。ブーツ３１９は、外筒端部３１９ａをカップ３１に嵌合して締結バンド等で固定する。一方、内筒端部３１９ｂをシャフト１２１に締結バンド等で固定する。   A lubricant (not shown) such as grease is sealed in this sealed space. The boot 319 is fitted with the outer cylinder end 319a to the cup 31 and fixed with a fastening band or the like. On the other hand, the inner cylinder end 319b is fixed to the shaft 121 with a fastening band or the like.

また、シャフト１２１は、等速ジョイント５の内輪側に連結されている。等速ジョイント５は、外輪のカップ５１と軸部５２が一体構造となっている。   The shaft 121 is connected to the inner ring side of the constant velocity joint 5. In the constant velocity joint 5, an outer ring cup 51 and a shaft portion 52 have an integral structure.

外輪のカップ５１の内面および内輪５１３の外面に軸方向の複数のトラック溝５１４、５１５を形成している。トラック溝５１４、５１５間に組み込んだボール５１６をケージ５１７で支持し、このケージ５１７の外周を外輪のカップ５１の内周に適合する球面とし、かつ内周を内輪５１３の外周に適合する球面としている。   A plurality of track grooves 514 and 515 in the axial direction are formed on the inner surface of the outer ring cup 51 and the outer surface of the inner ring 513. A ball 516 incorporated between the track grooves 514 and 515 is supported by a cage 517, and the outer periphery of the cage 517 is a spherical surface that fits the inner circumference of the cup 51 of the outer ring, and the inner circumference is a spherical face that fits the outer circumference of the inner ring 513 Yes.

外輪のカップ５１から、内輪５１３に連結されたシャフト１２１にかけて、ゴム組成物や樹脂の成形体であるブーツ５１９が装着されている。   A boot 519, which is a molded body of a rubber composition or a resin, is mounted from the cup 51 of the outer ring to the shaft 121 connected to the inner ring 513.

ブーツ５１９は、外輪のカップ５１に嵌合されて固定される外筒端部（大径取付部）５１９ａと、内輪に連結されたシャフト１２１に嵌合されて固定される内筒端部（小径取付部）５１９ｂと、これら外筒端部５１９ａと内筒端部５１９ｂとの間を繋ぐ複数の山谷を有する蛇腹状の屈曲部５１９ｃとを備え、等速ジョイント５を密封するように覆うものである。   The boot 519 includes an outer cylinder end portion (large diameter mounting portion) 519a that is fitted and fixed to the cup 51 of the outer ring, and an inner cylinder end portion (small diameter) that is fitted and fixed to the shaft 121 connected to the inner ring. (Attachment part) 519b and a bellows-like bent part 519c having a plurality of peaks and valleys connecting between the outer cylinder end part 519a and the inner cylinder end part 519b, and covers the constant velocity joint 5 so as to be sealed. is there.

この密封空間に、グリースなどの潤滑剤（図示省略）が封入されている。ブーツ５１９は、外筒端部５１９ａをカップ５１に嵌合して締結バンド等で固定する。一方、内筒端部５１９ｂをシャフト１２１に締結バンド等で固定する。   A lubricant (not shown) such as grease is sealed in this sealed space. The boot 519 is fixed with a fastening band or the like by fitting the outer cylinder end 519 a to the cup 51. On the other hand, the inner cylinder end 519b is fixed to the shaft 121 with a fastening band or the like.

このように、ドライブシャフトにもこの発明は適用することができ、ドライブシャフトの重量を軽減することが可能となる。また、上記した実施形態では摺動式等速ジョイントとして、トルク伝達部材がボールを用いたボールタイプのダブルオフセット型等速ジョイント（ＤＯＪ）を例示したが、トルク伝達部材としてローラを用いたローラタイプのトリポード型等速ジョイント（ＴＪ）であってもよい。また、サポート軸受４として転動体にボール４３を使った例を示したが、これに限らずローラであってもよく、転がり軸受であればよい。   Thus, the present invention can also be applied to the drive shaft, and the weight of the drive shaft can be reduced. In the above-described embodiment, the ball type double offset constant velocity joint (DOJ) using a ball as the torque transmission member is exemplified as the sliding constant velocity joint. However, the roller type using a roller as the torque transmission member. The tripod type constant velocity joint (TJ) may be used. Moreover, although the example which used the ball | bowl 43 for the rolling element as the support bearing 4 was shown, not only this but a roller may be sufficient and what is necessary is just a rolling bearing.

３ 等速ジョイント
４ サポート軸受
３１ カップ
３２ 軸部
３３ ボール転走面
３４ シール接触面
４２ 外輪
４３ ボール
４４ 保持器
４５ 軸受シール 3 Constant velocity joint 4 Support bearing 31 Cup 32 Shaft 33 Ball rolling surface 34 Seal contact surface 42 Outer ring 43 Ball 44 Cage 45 Bearing seal

Claims (5)

インボード側の等速ジョイントの外輪の軸部の外径面に、サポート軸受の転走面が形成され、この転走面の溝底の径がインボード側の等速ジョイントの外輪の軸部の最大径より小さく、この転走面と対向するように、サポート軸受用外輪が配置され、前記転走面とサポート軸受用外輪の転走面との間に、保持器で保持された複数の転動体が配置されていることを特徴とする等速ジョイントのサポート軸受。 A rolling surface of the support bearing is formed on the outer diameter surface of the shaft portion of the outer ring of the constant velocity joint on the inboard side, and the diameter of the groove bottom of this rolling surface is the axis of the outer ring of the constant velocity joint on the inboard side. smaller than the maximum diameter of the section, so that the rolling surface facing this, is arranged outer ring support bearing, between the rolling run surface of the outer ring for the rolling surface and support bearing, held by the retainer A support bearing for a constant velocity joint, wherein a plurality of rolling elements are arranged. 前記転走面を挟むようにシール接触面が設けられていることを特徴とする請求項１に記載の等速ジョイントのサポート軸受。   The support bearing for the constant velocity joint according to claim 1, wherein a seal contact surface is provided so as to sandwich the rolling surface. 前記転走面とシール接触面が高周波焼き入れにより硬化させたことを特徴とする請求項２に記載の等速ジョイントのサポート軸受。   The support bearing for the constant velocity joint according to claim 2, wherein the rolling contact surface and the seal contact surface are hardened by induction hardening. 前記保持器が樹脂製保持器であることを特徴とする請求項１に記載の等速ジョイントのサポート軸受。   The constant velocity joint support bearing according to claim 1, wherein the cage is a resin cage. インボード側の等速ジョイントの外輪であって、外輪はカップと軸部が一体構造になっており、前記カップの内面にはトルク伝達部材が転動する複数の直線状のトラック溝が形成され、軸部の外径面にサポート軸受の転走面が形成され、この転走面の溝底の径がインボード側の等速ジョイントの外輪の軸部の最大径より小さいことを特徴とする等速ジョイントの外輪。 An outer ring of a constant velocity joint on the inboard side, and the outer ring has a cup and a shaft part integrally formed, and a plurality of linear track grooves on which a torque transmission member rolls are formed on the inner surface of the cup. The rolling surface of the support bearing is formed on the outer diameter surface of the shaft portion, and the diameter of the groove bottom of the rolling surface is smaller than the maximum diameter of the shaft portion of the outer ring of the constant velocity joint on the inboard side. Outer ring of constant velocity joint.
JP2014144680A 2014-07-15 2014-07-15 Constant velocity joint support bearing and constant velocity joint outer ring Expired - Fee Related JP6306458B2 (en)

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JP2014144680A JP6306458B2 (en) 2014-07-15 2014-07-15 Constant velocity joint support bearing and constant velocity joint outer ring
CN201580038088.9A CN106536950B (en) 2014-07-15 2015-07-10 The bearing support of constant velocity cardan joint and the outer ring of constant velocity cardan joint
EP15822425.3A EP3171046A4 (en) 2014-07-15 2015-07-10 Support bearing for constant velocity joint, and outer ring for constant velocity joint
PCT/JP2015/069897 WO2016009960A1 (en) 2014-07-15 2015-07-10 Support bearing for constant velocity joint, and outer ring for constant velocity joint
US15/324,056 US20170204898A1 (en) 2014-07-15 2015-07-10 Support bearing for constant velocity joint, and outer ring for constant velocity joint

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US20170204898A1 (en) 2017-07-20
EP3171046A1 (en) 2017-05-24
WO2016009960A1 (en) 2016-01-21
CN106536950B (en) 2019-01-11
EP3171046A4 (en) 2018-07-11
CN106536950A (en) 2017-03-22

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